Storage arrangement and vehicle seat with storage arrangement

Abstract

Bearing arrangement (2) for two components (4, 34) pivotable relative to each other about an axis of rotation (12), in particular of a vehicle seat (40), comprising a component (4) with a bearing opening (6) in which a bearing bushing (8) extending in a longitudinal direction (L) and along the axis of rotation (12) is arranged with a circumferential bushing wall (22), wherein the bearing bushing (8) has a number of radially elastic areas (16) for radial tolerance compensation, wherein the bushing wall (22) is circular in cross-section except for the radially elastic areas (16) and is free of slots, characterized in that each radially elastic area (16) is formed by a radially elastic wall section (18) of the bushing wall (22) projecting radially inwards in the direction of the axis of rotation (12), and a material recess (20) is formed in the bushing wall (22) in the area of ​​the projecting wall section (18). is.

Description

The invention relates to a bearing arrangement for two components, in particular of a vehicle seat, which can be pivoted relative to one another about an axis of rotation, and also to a vehicle seat having such a bearing arrangement.A vehicle seat usually has an adjustment mechanism with a plurality of components that are adjustable relative to one another. For example, a backrest is rotatable relative to a seat. For this purpose, suitable bearing arrangements are provided in which, as a rule, the one component has a bearing opening into which a bearing bush is inserted. The component slides on the bearing bush, for example, during the pivoting movement.In this case, the highest possible accuracy of fit is important in order to avoid a bearing clearance at the bearing point, that is to say between the bearing bush and the component. Due to manufacturing tolerances, the bearing point is conventionally subject to either bearing play or an overpressing depending on the tolerance position. Bearing play can lead to noises, for example, and is also disadvantageous for the service life. Overpressing leads to increased friction and rigidity and loads the bearing point and, for example, also electric drives for seat adjustment. There is also the risk here that a bearing bolt designed as a threaded bolt, which is passed through the bearing point, can become detached over the course of time during the pivoting movement.Such a bearing arrangement for a vehicle seat can be taken from DE 10 2006 060 829 B4, for example. For axial and radial play compensation, the bearing bush described therein has resilient portions.Specifically, the bearing bush has a barrel-shaped bush section which is somewhat compressed during assembly, so that a prestressed barrel spring is formed.DE 103 11 679 A1 discloses a seat mechanism of a vehicle seat having a bearing arrangement, in which a play compensation element is provided at the bearing point, which play compensation element has a plurality of spring regions which engage into a bearing gap. The spring elements are designed as bent spring tabs which are integrally formed on a common annular base body.DE 10 2009 011 045 B4 shows a bearing bush in which spring tongues cut free from an inner wall protrude.EP 2 250 046 B1 discloses a bearing bush in which a collar which is offset outwards and has spreading means attached there is then connected to a bearing surface.EP 2 505 850 B1 describes a bearing bush having a bearing region which is corrugated when viewed in cross section and has radially outward protrusions and radially inward sector portions having contact surfaces.DE 299 24 397 U1 discloses a pot-shaped bearing bush which has elastic elements by means of which an inserted tube is prestressed and centered in the axial and radial direction.DE 10 2006 008 603 B3 and WO 2005 / 005 847 A1 each disclose bearing arrangements without bearing bushes, in which a bearing eye is formed in a bearing plate, on which elastically deformable projections and / or weakened regions formed by recesses are formed.Proceeding from this, the object of the invention is to specify a bearing arrangement for a vehicle seat and a vehicle seat having such a bearing arrangement, wherein reliable radial tolerance compensation is ensured by means of structurally simple means.The object is achieved according to the invention by a bearing arrangement for two components, in particular a vehicle seat, which are pivotable relative to one another about an axis of rotation, wherein the one component has a bearing opening in which a bearing bush, which extends in a longitudinal direction and along the axis of rotation and has a circumferential bush wall, is arranged, which bush wall has a number of radially elastic regions (that is to say at least one or more regions) for a radial tolerance compensation, wherein a respective radially elastic region is formed by a radially elastic wall section of the bush wall which projects radially inward in the direction of the axis of rotation.Projecting wall section is understood here in particular to mean a part of the continuous bushing wall which in particular does not have any cut-outs or slots or the like. The protruding wall section is therefore a part of the continuous uninterrupted bushing wall and, for example, not a bent-out, spring-elastic tab which is virtually cut out of the bushing wall and is only connected to the latter by a foot region. The bushing wall is therefore free of slots overall.The bearing bush is regularly designed for a nominal radius, i.e. has an inner wall which-apart from the radially elastic regions-is circular in cross section and is generally typically cylindrical with the nominal radius. The inwardly projecting wall sections reduce the diameter in these regions, so that in a respective radially elastic region the radius or diameter present there is reduced in comparison to the nominal radius or nominal diameter. A respective radially elastic region preferably forms a punctiform and in particular linear contact with the bearing partner, especially with the component.The individual protruding wall sections are in this respect discrete, individual partial regions of the bushing wall which extend in the circumferential direction only over a limited angular range and thus just not circumferentially. A respective wall section extends, for example, at most over an angle range of less than 90°, preferably of less than 45° or also less than 30° and in some embodiment variants also only up to at most 10°.In the longitudinal direction, the projecting wall section preferably extends over the entire length of the bearing bush. In particular, the wall section achieves an in particular linear contact with the component over the entire length. Alternatively, the protruding wall portion extends over only a portion of the entire length.Due to the elastic configuration in the radial direction, these radially elastic regions therefore reliably equalize a tolerance play during assembly. Due to the point- or line-shaped contact, at the same time only a slight pressing is formed locally. This ensures a mounting which is largely free from play and thus has low noise while at the same time ensuring the greatest possible ease of movement. The radially elastic region therefore compensates for the production-related diameter tolerances. Furthermore, micromovements of the components can be damped by the elastic regions, especially when the load changes.Overall, therefore, less friction is achieved compared with a conventional bearing point with a bearing interference, the risk of loosening the threaded bolt is low and the bearing point is smooth overall. Due to the mounting which is largely free from play, bearing noises are avoided. In addition, in the case of micromovements of the two bearing partners in the radial direction, these movements are damped. In addition, the bearing bush is overall robust and can easily be produced from a manufacturing standpoint, for example as an injection-molded component.In a preferred embodiment, the bushing wall has an inner wall which is flattened in sections to form the radially elastic wall section and thus, viewed in a plan view, runs in particular in a straight line. Viewed in a plan view or in cross section, the radially elastic wall section is therefore formed by a saw edge of a circle.In the region of a respective protruding wall section, a material recess is formed in the bushing wall. Here, a material recess in the bushing wall is understood to mean that the material recess is surrounded completely circumferentially by material of the bushing wall. The material recess is therefore a hole in the bushing wall, which is formed, for example, as a blind hole or also as a through hole, which extends over the entire length of the bushing in the longitudinal direction. Overall, this material recess has the effect that the projecting wall section can easily escape outward in the radial direction. The wall section can therefore escape into the free space formed by the material recess within the bushing wall. At the same time, the outer periphery of the bearing bush is closed in a circumferential manner by an outer wall, so that overall good and high stability of the bearing bush is achieved.As an alternative to this configuration with the material recesses introduced in the bushing wall, the (entire) bushing wall is deformed radially inward in the region of the wall sections, for example in the manner of embossed knobs or ribs.In a preferred embodiment, a respective material recess is formed by an elongated hole-as viewed in a plan view-which has, as viewed in cross section, in particular a rectangular geometry. The elongated hole runs with its longitudinal sides in particular parallel to the wall section (leaflet) described above. The length of the elongated hole in the circumferential direction corresponds to the length of the wall section in the circumferential direction, thus in particular to the length of the floss. Preferably, the length of the elongated hole is somewhat greater than that of the wall section and is, for example, at most 20% greater than it.A respective slot extends in the circumferential direction, for example, over an angular range of at least 20° to a maximum of 45° and preferably in the range between 25° and 35°.As an alternative to the configuration as an elongated hole, the material recess has a circular cross-sectional shape.In a preferred development, a respective material recess is filled with an elastomeric material. For this purpose, either a separate element made of an elastomeric material is used or the elastomeric material is formed by a multi-component injection molding together with the remaining bearing bush. The introduction of the elastomeric material achieves the particular advantage that the stiffness and thus in particular the desired damping can be set and is preferably also set differently in a targeted manner and in particular for different applications.According to a preferred embodiment, the material recess extends continuously over the entire length through the bushing wall and is formed as a continuous hole.Alternatively, the material recess is formed only as a blind hole, which extends only over a limited longitudinal section, which lies, for example, in the range between 20% and 50% of the total length of the bearing bush.In a preferred embodiment, the bushing wall is furthermore formed as a solid wall made of solid material, wherein only a small number of radially elastic regions and thus preferably also of material recesses are formed distributed around the circumference. A small number is understood here to mean a number in the range between 1 and a maximum of 8 or a maximum of 10 and in particular a number in the range between 2 and 4. Especially when the material recesses are designed as circular recesses, more can also be provided. The radially elastic regions are preferably arranged in a uniformly distributed manner.According to a preferred embodiment, the bearing opening has a non-round contour with a number (at least one or more) of radial bulges, wherein a respective radially elastic region and thus a protruding wall section or a material recess is positioned at a respective one of these radial bulges. The radially elastic regions of the bushing wall are therefore each positioned at the same angular position as the radial protrusions. Preferably, the number of radial protrusions corresponds to the number of radially elastic regions distributed around the circumference.This configuration preferably forms an additional radial clearance, so that in the case of a radial compensating movement, the radial compensation can also take place into the bulge. Preferably, therefore, a radial distance is formed between the bushing outer wall and the radial bulge, so that an additional radial compensating path exists. The radial compensation therefore takes place not only inside the bushing wall, but also outside the bushing. The sleeve outer wall can therefore be deformed radially outwards under radial load in this embodiment.In a preferred embodiment, the protrusions simultaneously or alternatively also serve as a rotation prevention means and the bearing bush engages with radial projections in these protrusions, so that a positive connection which is effective in particular on both sides in the circumferential direction is formed.Especially in an embodiment variant in which the radially elastic wall sections extend in the longitudinal direction only over a partial region of the bearing bush, all the radially elastic wall sections are formed only on one end side and thus only on one side on one end side of the bearing bush.In this case, they are formed in particular as embossings, in which material of the bearing bush therefore projects radially inward in order to form the wall sections.These protruding wall sections preferably continuously merge again into the normal inner wall of the bushing with the nominal radius in the further course in the longitudinal direction and / or circumferential direction. In the region of these wall sections formed in the manner of embossings, the aforementioned blind-hole-shaped material recesses are formed in each case.The wall sections are preferably formed by a regional deformation and embossing of the bushing wall from an end side. For this purpose, the blind hole is introduced, for example, by means of a punch, and the material is thus deformed.The component is in particular a component which extends in the radial direction and is elongate and which thereby defines a lever axis which runs through the axis of rotation. At its end opposite the axis of rotation, the component is fastened in the installed state to a further bearing point or is also mounted such that it can be pivoted about a further axis of rotation, if appropriate. The lever axis runs through the axis of rotation and this further bearing point.According to a preferred embodiment, the component has two bearing openings, in each of which a bearing bush is inserted. The lever axis runs in each case through the axis of rotation of the bearing openings. The two bearing bushes are each designed as described above and in particular they are identical parts.According to a first embodiment variant, the at least one radially elastic wall section lies on the lever axis. Since the radial loads act in the direction of the lever axis, this measure absorbs any radial compensating movement that may be required directly at the location of the lever axis.According to a preferred alternative embodiment, at least one pair of radially elastic wall sections is formed, wherein this pair is arranged symmetrically to the lever axis. This further variant has the advantage that in the region of the lever axis in which the greatest loads occur, the bearing bush is not weakened by a material recess. At the same time, the symmetrical arrangement of the pair enables the radial compensating movement. The two pairs are spaced apart from the lever axis by an identical angular distance due to their symmetrical arrangement. This is, for example, in the range between 10° and 30°, wherein the angular distance is defined between the lever axis and the beginning of the wall section. The angular distance between the lever axis and a center of the wall section is correspondingly greater and light, for example in the range from 20° to 60° and in particular at 45°.In a preferred embodiment, a pair of radially elastic wall sections is formed on one circumferential side only on one side or alternatively a pair of radially elastic wall sections are formed on opposite circumferential sides and thus exactly one pair of radially elastic wall sections on each side. The lever axis extends symmetrically through a respective pair.In addition to the at least one bearing opening, the component preferably has an anti-rotation element spaced apart from the bearing opening, for example in the form of a recess extending in the longitudinal direction or else of a pin, and the bearing bush has a radial arm with a corresponding anti-rotation element, for example a pin or a recess. The corresponding anti-rotation elements engage in one another. This measure provides a reliable anti-rotation means with a large lever arm.According to a preferred embodiment, axial tolerance compensation elements are formed for axial tolerance compensation in addition to the radially elastic regions. As a result, both axial and radial compensating movements and, in particular, tolerance compensations during assembly are therefore made possible. In the region of the axial tolerance compensation elements, in particular no wall sections projecting radially inward are formed on the inner wall of the bushing.The axial tolerance compensation elements are preferably designed as elastic elements. They are arranged circumferentially, in particular in a uniformly distributed manner, on the end face of the bearing bush.In a preferred embodiment, they are designed as an in particular cylindrical material projection. In this embodiment as well, similar to the radially elastic regions, the axial tolerance compensation is preferably effected by elastic deformation.In a preferred embodiment, the radially elastic regions and the axial tolerance compensation elements are formed alternately in the circumferential direction, at least one axial tolerance compensation element being formed between two adjacent radially elastic regions.The component into which the bearing bush is inserted is generally, in a preferred embodiment, a metal part. In contrast, the bearing bush is generally a plastic part. This is, for example, cast directly onto the component. Alternatively, it is inserted as a separately produced element as a prefabricated component into the bearing opening of the component.The component is in particular a part of a seat mechanism of a vehicle seat which is installed in a motor vehicle in the final assembled state. Specifically, it is for example a lever, a rocker or another support element of the seat mechanism. The component can itself be the pivotable element, which pivots about the axis of rotation. Alternatively, it is a non-pivotable, fixed part, such as a base of the vehicle seat, especially a side part of such a base. This is connected, for example, directly to a vehicle floor of the vehicle or is also arranged on a rail system for longitudinal adjustment.Embodiments of the invention are illustrated in more detail below with reference to the figures. These are shown in partially simplified representations: FIG. 1 shows a bearing arrangement of a vehicle seat with a component which has two bearing openings with bearing bushes inserted therein, according to a first variant embodiment, FIG. 2 shows a bearing arrangement as in FIG. 1, but with bearing bushes according to a second embodiment variant, FIG. 3 shows a detail illustration of the component in the region of a bearing bush, FIG. 4 shows a detail illustration of the component with inserted bearing bush of a first embodiment variant, FIG. 5 shows a detail illustration of the component with inserted bearing bush of a second embodiment variant, FIG. 6A shows a detail illustration of the component with inserted bearing bush of a third embodiment variant, FIG. 6B shows a detail enlarged illustration of FIG. 6A, FIG. 7 shows a simplified cross-sectional illustration through a bearing arrangement, and FIG. 8 shows a greatly simplified side illustration of a vehicle seat.A bearing arrangement 2 illustrated by way of example in FIG. 1 and in FIG. 2 has an elongate component 4 which, in the exemplary embodiment, extends in an arcuate manner. In the exemplary embodiment, this component 4 has in each case in its opposite end regions a bearing opening 6, in which a bearing bush 8 is arranged in each case. In addition to the two bearing openings 6, the component 4 in the exemplary embodiment has further (optional) recesses 10, in particular as circular passage openings, which can be used as abutments for a specially designed bearing bush 8 for preventing rotation, if required.Each of the two bearing openings 6 defines a centrally arranged axis of rotation 12 which at the same time defines a longitudinal direction L which extends into the plane of the paper in FIGS. 1 and 2. A lever axle 14 runs through the two axes of rotation 12.In the exemplary embodiments shown, a respective bearing bush 8 has a substantially cylindrical bush part 8A extending in the longitudinal direction L and preferably a radially protruding annular flange 8B formed on an end side, which covers an opening edge of the bearing openings 6.The respective bearing bush 8 has a specific configuration for a radial tolerance compensation and is in particular also able to absorb and in particular damp (micro)moves in the radial direction and specifically in the direction of the lever axis 14. In addition, the bearing bush 8 is also designed for axial tolerance compensation.For the radial tolerance compensation, a respective bearing bush 8 has at least one and preferably a plurality of radially elastic regions 16. In all variant embodiments, a respective radially elastic region 16 has a wall section 18 projecting inward in the direction of the axis of rotation 12 and a material recess 20 associated with the respective wall section 18 within a bushing wall 22 of the bushing 8. The bushing wall 22 simultaneously forms the bushing part 8A. It is formed solid from solid material apart from the material recesses 20, and is in particular substantially cylindrical, i.e. has a cylindrical inner wall 24 apart from the protruding wall portions 18.In the embodiment variants according to FIGS. 1, 2, 3 to 4, the wall section 18 is formed by a flattened partial region of the bushing wall 22. Viewed in a plan view (as viewed in the longitudinal direction L), the wall section 18 therefore runs along a line and thus forms a segregant of a circle otherwise formed by the inner wall 24 and having a nominal radius.The bearing opening 6 preferably has a non-round geometry and in particular has radially outwardly shaped bulges 26, which serve for anti-rotation and / or as a radial compensation space.With regard to the function of the anti-rotation device, the respective bearing bush 8 has radial projections on its bush part 8A, namely on its outer wall, not shown in any more detail here, which engage positively in the recesses 26 in the circumferential direction, so that the bearing bush 8 is held in a rotationally fixed manner.The radially elastic regions 16 of the bearing bush 8 are arranged at the same angular position as the bulges 26.Between an outer wall of the bushing part 8A and the wall of the bulge 26, a radial distance is preferably formed in the radial direction. In the event of a radial load, the bushing wall can therefore be bent radially outwards into these bulges 26 at the position of the flexible regions 16. In this embodiment variant, therefore, the deformation of the radially elastic region 16 does not necessarily have to be compensated solely by the bushing wall 22, but rather can also be accommodated by a region outside the bushing 8.In the exemplary embodiments according to FIGS. 1 to 4, the recesses 20 are formed as elongated holes, the two opposing long sides of which preferably run in a straight line and in particular parallel to the protruding wall section 18. The recesses 20 extend over an angular range which is equal to and in particular greater (up to, for example, at most 1.2 times) than the angular range over which the respective protruding wall section 18 extends. The recess 20 forms only a thin partition wall, which defines the wall section 18. This can therefore easily yield elastically outwards in the radial direction. It can therefore deform into the recess 20.As can be seen from FIG. 1, a pair of radially elastic regions 16 is arranged in each case symmetrically with respect to the lever axis 14. Especially in the case of non-driven levers or rockers, the load, i.e. either a tensile load or a compressive load, acts as the component 4 in the direction of the lever axis 14. FIG. 1 shows an embodiment variant in which each bearing bush 8 has in each case (exactly) two opposite pairs of radially elastic regions 16.The two radially elastic regions 16 of a respective pair are arranged, for example, at an angle of between 45° and 90° with respect to one another. Preferably, the (exactly) four radially elastic regions 16 are preferably arranged in a uniformly distributed manner.FIG. 2 shows, in contrast, an embodiment variant in which a radially elastic region 16 and thus also the material recess 20 is arranged centrally on the lever axis 14. In such a variant, particularly good damping is achieved. A portion of the forces is thereby divided into the regions next to the flexible region 16, as is shown by the arrows.In the embodiment variant according to FIG. 2, a respective bearing bush 8 generally has exactly one radially elastic region 16. In the case of the two bearing bushes 8 and the two bearing points, these are oriented at opposite positions along the lever axis 14, i.e. the two bearing bushes 8 are rotated relative to one another by 180° about the axis of rotation 14.Analogously to FIG. 2, in an alternative configuration, in the case of a symmetrical arrangement in pairs, as is illustrated in FIG. 1, only one pair is arranged on one side, with the result that only one pair of radially elastic regions 16 is formed per bearing bush 8. In this variant, too, the two bearing bushes 8 are arranged in particular rotated by 180° with respect to one another.As an alternative to the embodiment according to FIG. 2, exactly two radially elastic regions 16 are arranged opposite each other per bearing bush 8, each of which regions lies on the lever axis 14.According to a preferred embodiment variant, the material recesses 20 are filled with an elastomeric material 28. This is illustrated by way of example in the case of one of the material recesses 20 in FIG. 4. The elastomeric material 28 serves in particular for adjusting the elastic properties (stiffness) and / or the damping properties. The elastomeric material 28 is inserted into a respective material recess 20, for example, as an independent separate element. Alternatively, it is formed directly during the formation of the bearing bush 8 in a multi-component injection molding.The embodiment variants shown in FIGS. 1, 2, 3 to 4 are used in particular in situations with defined load directions, in which a defined alignment of the radially elastic regions 16 with respect to the expected load directions is thus possible. Especially in such embodiments, therefore, only a limited number of, for example, 1 to 4 radially elastic regions 16 are provided.For components 4 with complex load situations, a larger number of, for example, at least 6, 8 or 10 radially elastic regions 16 are preferably arranged distributed in particular homogeneously around the circumference. The total number of radially elastic regions is preferably less than 16 overall also in this embodiment variant.In particular in such an embodiment variant, the material recesses 20 are preferably designed as circular holes, as is illustrated in FIG. 5. The respectively associated protruding wall sections 18 are designed in the manner of longitudinal ribs extending in the longitudinal direction L, which for example, in a plan view, project convexly curved inward in the direction of the axis of rotation 12.The holes are-analogously to the slots in the embodiment variant according to FIG. 4-formed as through-holes, which thus extend over the entire length of the bearing bush 8.In addition to the radially elastic regions 16, the respective bearing bush 8 additionally also has axial tolerance compensation elements 30. In the exemplary embodiment, these are formed by, in particular, cylindrical or knob-shaped material projections 32 which are formed at least on one end side and, in particular, in the region of the annular flange 8B. In the region of these axial tolerance compensation elements 30, there are preferably no wall sections on the inner wall which project in the direction of the axis of rotation 12. Rather, the inner wall 24 is formed cylindrically there and runs along a circular arc with the nominal radius.In conjunction with FIGS. 6A, 6B, a further variant embodiment is shown, which is particularly simple to produce. In this case, the respective radially elastic region 16 is formed only on one side on one of the opposite end sides of the bearing bush 8, and specifically in the region of the end side with the annular flange 8B. The individual radially elastic regions 16 are in turn formed by a wall section 18 projecting in the radial direction and a material recess 20 assigned thereto. The individual wall sections 18 are in this case formed in the manner of noses which in turn extend only over a limited angular range in the circumferential direction and at the same time also only over a limited longitudinal section in the longitudinal direction L. For example, they extend only over a range of 20%-50% of the length of the bearing bush 8.These radially elastic regions 16 are produced in particular by an embossing process in which the bearing bush 8 is embossed in each case only on one of the end sides. In this case, a material forming is preferably carried out from the end side with an embossing die, so that the material is displaced radially inward to form the described nose and at the same time the material recess 20 is formed. In the exemplary embodiment shown, elongated stamping geometries are shown and the material recess 20 is again formed in the manner of an elongated hole. Alternatively, circular stamping geometries with circular material recesses 20 can also be formed. The number and orientation of these flexible regions 16 can be selected-depending on requirements-analogously to the previously described embodiment variants.The embossing takes place, for example, directly during the process of injection-molding the component 2 to form the bearing bush 8 or else subsequently.As an alternative to the anti-rotation device with the non-round geometry of the bearing opening 6, explained in particular in connection with FIGS. 3 and 4, the bearing bush 8 has, in a configuration not shown here, a radially protruding arm which is configured in particular only on the end side and as a radial extension of the annular flange 8B. On this arm, an anti-rotation element is formed, which is formed corresponding to the anti-rotation element formed by the recess 10. That is, specifically as a pin which engages in the recess 10.FIG. 7 shows a detail illustration of a typical structure of the complete bearing arrangement 2 in the installed state. The component 4 is arranged such that it can be pivoted about the common axis of rotation 14 relative to a further component 34. For this purpose, the component 4 is typically pivotable relative to the bearing bush 8 arranged in its bearing opening 6. The further component 34 likewise has a passage opening which is arranged coaxially with respect to the axis of rotation 14. The two components 4, 34 are mounted on one another via an in particular step-shaped bearing bolt 36. This is in particular a screw which is screwed into a mounting part 38. This is connected, for example, rotationally fixedly to the further component 34.The illustrated bearing arrangement 2 is in particular part of a vehicle seat 40, as is illustrated in a greatly simplified manner in FIG. 8. In this case, a backrest 42 is arranged on a seat part 44 such that it can be pivoted about the axis of rotation 12, for example. The component 4 is, for example, a type of rocker in which, for example, the backrest 42 is pivotably fastened as the further component 34 at the rear bearing point, on the right-hand half of the figure shown in FIG. 1, with the bearing openings 6 and the bearing bush 8. Alternatively, this right bearing point can also be fastened directly to a fixed base. The front bearing point shown on the left half of the figure in FIG. 1 is, for example, pivotably fastened to a carrier element of the seat part 44 and, for example, part of a kinematic adjustment system of the seat part 44, which is associated, for example, with a height adjustment of the seat part 44.List of reference characters2 Bearing arrangement 4 Component 6 Bearing openings 8 Bearing bush 8A Bush part 8B Annular flange 10 Recess 12 Axis of rotation 14 Lever axis 16 Radially elastic region 18 Projecting wall section 20 Material recess 22 Bush wall 24 Inner wall 26 Bulge 28 Elastomeric material 30 Axial tolerance compensation element 32 Material projection 34 Further component 36 Bearing bolt 38 Mounting part 40 Vehicle seat 42 Backrest 44 Seat part L Longitudinal direction

Claims

Bearing arrangement (2) for two components (4, 34), in particular of a vehicle seat (40), which are pivotable relative to one another about an axis of rotation (12), comprising a component (4) having a bearing opening (6) in which a bearing bush (8) extending in a longitudinal direction (L) and along the axis of rotation (12) is arranged having a circumferential bush wall (22), wherein the bearing bush (8) has a number of radially elastic regions (16) for radial tolerance compensation, wherein the bush wall (22), apart from the radially elastic regions (16), is of circular cross section and is free of slots, characterized in that a respective radially elastic region (16) is formed by a radially elastic wall section (18) of the bush wall (22) which projects radially inwards in the direction of the axis of rotation (12), and a material recess (20) is formed in each case in the bush wall (22) in the region of the projecting wall section (18).Bearing arrangement (2) according to the preceding claim, characterized in that the bush wall (22) has an inner wall (24) which is flattened in the region of the wall section (18).Bearing arrangement (2) according to the preceding claim, characterized in that the respective material recess (20) is formed by an elongated hole.Bearing arrangement (2) according to one of Claims 1 to 2, characterized in that the respective material cutout (20) has a circular cross-sectional shape.Bearing arrangement (2) according to one of the preceding claims, characterized in that the respective material recess (20) is filled with an elastomeric material (28).Bearing arrangement (2) according to one of the preceding claims, characterized in that the respective material recess (20) is formed as a hole which is continuous in the longitudinal direction (L) or as a blind hole in the bush wall (22).Bearing arrangement (2) according to one of the preceding claims, characterized in that the bush wall (22) is solid and only a small number of radially elastic wall sections (18) is distributed around the circumference, wherein the number is between 1 and 8 and preferably between 2 and 4.Bearing arrangement (2) according to one of the preceding claims, characterized in that the bearing opening (6) has a non-round contour with a number of radial bulges (26), wherein a respective radially elastic region (16) is positioned at a respective radial bulge (26).Bearing arrangement (2) according to one of the preceding claims, characterized in that a respective radially elastic wall section (18) extends in the longitudinal direction (L) only over a partial region of the bearing bush (8), and all radially elastic wall sections (18) are formed only on one side on an end side of the bearing bush (8) and in particular as embossings.Bearing arrangement (2) according to one of the preceding claims, characterized in that the component (4) is a component (4) which is elongate in the radial direction and which defines a lever axis (14) running through the axis of rotation (12), wherein the at least one radially elastic wall section (18) lies on the lever axis (14) or at least one pair of radially elastic wall sections (18) is arranged symmetrically with respect to the lever axis (14).Bearing arrangement (2) according to the preceding claim, characterized in that the component (4) has two bearing openings (6), in each of which a bearing bush (8) is inserted, wherein the lever axis (14) in each case runs through the axis of rotation (12) of the bearing openings (6).Bearing arrangement (2) according to one of the preceding claims, characterized in that a pair of radially elastic wall sections (18) is formed only on one side or exactly one pair of radially elastic wall sections (18) is formed on each side opposite.Bearing arrangement (2) according to one of the preceding claims, characterized in that axial tolerance compensation elements (30) are formed in addition to the radially elastic regions (16).Bearing arrangement (2) according to the preceding claim, characterized in that the axial tolerance compensation elements (30) are each formed on an axial end face of the bearing bush (8) as an in particular cylindrical material projection (32).Bearing arrangement (2) according to one of the two preceding claims, characterized in that at least one axial tolerance compensation element (30) is arranged in each case between adjacent radially elastic regions (16).Vehicle seat (40) having a bearing arrangement (2) according to one of the preceding claims.

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